CN106050655A - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
CN106050655A
CN106050655A CN201610149553.2A CN201610149553A CN106050655A CN 106050655 A CN106050655 A CN 106050655A CN 201610149553 A CN201610149553 A CN 201610149553A CN 106050655 A CN106050655 A CN 106050655A
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CN
China
Prior art keywords
chamfered section
tabular
section
scroll
screw compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201610149553.2A
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Chinese (zh)
Other versions
CN106050655B (en
Inventor
长冈文
长冈文一
茗原将史
鸣海圭亮
鹤冈洋佑
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of CN106050655A publication Critical patent/CN106050655A/en
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Publication of CN106050655B publication Critical patent/CN106050655B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/007—Sealings for working fluid between radially and axially moving parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/40—Heat treatment
    • F04C2230/41—Hardening; Annealing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/10—Hardness

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The present invention relates to a scroll compressor (100) includes a chamfered portion (1M) formed on the fixed scroll member (1) plate-shaped vortex teeth (1b) the distal end portion of the chamfered portion (2m), which is formed in the swing scroll (2) the plate-shaped distal end portion of the vortex ring (2b) 1.51; the chamfered portion, which is formed on the plate-shaped vortex teeth (1b) of the root, and the shape of the chamfered portion (2m) the same shape, and a chamfered part (2n), which is formed on the plate-shaped vortex teeth (2B) the shape of the root, and the chamfered part is the same as the shape of (1m).

Description

Screw compressor
Technical field
The present invention relates to achieve the refrigerant gas in compression process from pressing down that discharge chambe leaks The screw compressor of system.
Background technology
In the past, propose have a kind of achieving that the refrigerant gas in compression process is leaked from discharge chambe The screw compressor of suppression.As this existing screw compressor, such as, propose there is following whirlpool Revolving compressor, it is formed multiple discharge chambe by fixed scroll (scroll) and swing scroll, Described fixed scroll has circinate tabular whirlpool tooth, described pendulum at seat board (bed plate) Dynamic scroll has and the tabular whirlpool of engagement opposed with the tabular whirlpool tooth of described fixed scroll Tooth, makes volume because of the oscillating motion of above-mentioned swing scroll towards the center of above-mentioned discharge chambe Reducing while being compressed, being formed with chamfering in the tabular whirlpool tooth top end of above-mentioned swing scroll Portion, the tabular whirlpool tooth outer wall root in above-mentioned fixed scroll be formed recess (for example, referring to Patent documentation 1).
Patent documentation 1: Japanese Unexamined Patent Publication 2012-137000 publication
For the screw compressor described in patent documentation 1, for the tabular swinging scroll The chamfered section of whirlpool tooth top end and the tabular whirlpool tooth outer wall root of fixed scroll are (with swing The position that the chamfered section of the tabular whirlpool tooth top end of scroll is opposed) recess, and undefined suitable When size relationship.It addition, for the screw compressor described in patent documentation 1, not Define the tabular whirlpool tooth top end of fixed scroll especially and swing the tabular whirlpool of scroll The shape of tooth outer wall root (position opposed with the tabular whirlpool tooth top end of fixed scroll). Therefore, there is following problem in the screw compressor described in patent documentation 1: sometimes at whirlpool tooth top The gap formed between end and whirlpool root portion increases so that the refrigerant gas in compression process is let out The amount of leakage increases, thus causes leakage loss to be aggravated.
Summary of the invention
The present invention produces to solve problem as above, and its object is to acquisition can Refrigerant gas in suppression compression process is from tabular whirlpool tooth top end and tabular whirlpool root portion Between leak such that it is able to suppression leakage loss aggravation screw compressor.
Screw compressor involved in the present invention possesses: fixed scroll, its have the first seat board portion, And the first tabular whirlpool tooth of setting is erected in a face in this first seat board portion；Swing scroll, It has the second seat board portion and opposed with described fixed scroll in this second seat board portion The face of side erects the second tabular whirlpool tooth of setting, described first tabular whirlpool tooth and described second tabular Whirlpool tooth engages and forms discharge chambe, and this swing scroll swings relative to described fixed scroll Motion；First chamfered section, it is formed at two corners of top ends of described first tabular whirlpool tooth； Second chamfered section, it is formed at two corners of top ends of described second tabular whirlpool tooth；3rd falls Corner, it is formed at the root both sides of described first tabular whirlpool tooth, the shape of the 3rd chamfered section with The shape of described second chamfered section is identical；And the 4th chamfered section, it is formed at described second tabular whirlpool The root both sides of whirlpool tooth, the shape of the 4th chamfered section is identical with the shape of described first chamfered section, institute The chamfer dimesion stating the first chamfered section is different from the chamfer dimesion of described second chamfered section.
Preferably, described fixed scroll is formed by the material that hardness is different from described swing scroll, The chamfer dimesion of the side that hardness in described 3rd chamfered section and described 4th chamfered section is high big and The chamfer dimesion of the side that hardness is low is little.
Preferably, described first chamfered section, described second chamfered section, described 3rd chamfered section and Described 4th chamfered section is formed as the chamfer shape that cross section is linearity.
Preferably, described first chamfered section, described second chamfered section, described 3rd chamfered section and Described 4th chamfered section is formed as the chamfer shape that cross section is arc-shaped.
Preferably, pass through observing the oscillation center from described swing scroll, and along described first In the cross section erecting setting direction of tabular whirlpool tooth and described second tabular whirlpool tooth, described pressure Under the state in the cross section that the sectional area of contracting room is maximum, when by described first chamfered section and described 4th chamfering The sky being formed between described first chamfered section and described 4th chamfered section under the immediate state in portion Between sectional area be defined as Av1, by described second chamfered section and the described 3rd immediate shape of chamfered section The sectional area in the space being formed between described second chamfered section and described 3rd chamfered section under state is fixed When justice is Av2 and the sectional area of described discharge chambe is defined as Ac, described screw compressor sets It is 0 ＜ { (Av1+Av2)/2}/Ac ＜ 1 × 10-4。
Preferably, described chamfer dimesion is the size of described chamfered section.
In screw compressor involved in the present invention, by the first tabular whirlpool tooth top of fixed scroll The shape of the first chamfered section of end and the 4th of the second tabular whirlpool root portion of swing scroll the The shape of the position that the shape of chamfered section is i.e. opposed with the first chamfered section is set to same shape.It addition, The shape of the second chamfered section of the second tabular whirlpool tooth top end of scroll and fixing whirlpool will be swung The shape of the 3rd chamfered section of the first tabular whirlpool root portion of rotating part is i.e. opposed with the second chamfered section The shape of position be set to same shape.Therefore, screw compressor involved in the present invention can press down Refrigerant gas in compression process processed from tabular whirlpool tooth top end and tabular whirlpool root portion it Between leak such that it is able to suppression leakage loss aggravation.Therefore, the present invention is capable of efficiently Screw compressor.
Accompanying drawing explanation
Fig. 1 is the longitudinal section illustrating the screw compressor involved by embodiments of the present invention 1.
Fig. 2 is to illustrate near the discharge chambe of the screw compressor involved by embodiments of the present invention 1 Longitudinal section.
Fig. 3 is the A portion enlarged drawing in Fig. 2.
Fig. 4 is the B portion enlarged drawing in Fig. 2.
Fig. 5 be illustrate the Av/Ac of the screw compressor involved by embodiments of the present invention 1 with The figure of the relation of compressor performance.
Fig. 6 is to illustrate in Fig. 5 the existing scroll compression used in the calculating of compressor performance ratio The major part enlarged drawing of the tabular whirlpool odontoid of machine.
Fig. 7 be illustrate the C1m/H of the screw compressor involved by embodiments of the present invention 1 with The figure of the relation of compressor performance.
Fig. 8 be illustrate the Dc1/Ds of the screw compressor involved by embodiments of the present invention 1 with The figure of the relation of compressor performance.
Fig. 9 is to illustrate near the discharge chambe of the screw compressor involved by embodiments of the present invention 2 Longitudinal section.
Figure 10 is the C portion enlarged drawing in Fig. 9.
Figure 11 is the D portion enlarged drawing in Fig. 9.
Description of reference numerals:
1 ... fixed scroll；1a ... seat board portion；1b ... tabular whirlpool tooth；1c ... crosshead guiding groove； 1d ... outlet；1e ... suction inlet；1f ... discharge chambe；1h ... top ends；1k ... root；1m… Chamfered section；1n ... chamfered section；2 ... swing scroll；2a ... seat board portion；2b ... tabular whirlpool tooth； 2c ... crosshead guiding groove；2d ... oscillation bearing；2e ... aspirating hole；2f ... thrust face；2g ... convex Platform portion outer space；2h ... top ends；2k ... root；2m ... chamfered section；2n ... chamfered section； 2o ... seat board peripheral part space；3 ... flexible frame；3a ... thrust bearing；3b ... face；3c ... main Bearing；3d ... auxiliary spindle holds；3e ... intercommunicating pore；3f ... intercommunicating pore；3g ... intermediate pressure adjusts Valve；3h ... intermediate pressure adjusts valve pressing piece；3k ... intermediate pressure adjusts spring；3m ... connection Hole；3n ... intermediate pressure adjusts valve accommodation space；3p ... upper barrel surface；3s ... lower barrel surface；3t… Thrust bearing peristome；3v ... lower surface；4 ... guiding frame；4a ... framework upper space；4b… Lower frame space；4c ... upper barrel surface；4d ... lower barrel surface；4f ... the first path；4g ... the One drain passageway；5 ... motor；5a ... rotor；5b ... stator；5f ... through stream；5g… Alternate path；5h ... wire；6 ... main shaft；6a ... swinging axle portion；6b ... main shaft part；6c ... secondary Axle portion；6d ... oil-feed port；6e ... high pressure oil supply hole；6f ... principal axis balance counterweight；6g ... supply Oilhole；7a ... annular seal；7b ... annular seal；8 ... sub-frame；8a ... supplementary bearing；9… Crosshead mechanism；9a ... fixing side switch；9b ... swing side switch；9c ... crosshead mechanism annulus； 10 ... hermetic container；10a ... high-pressure space；10b ... glass terminal；11 ... refrigerator oil；12… Discharge pipe；13 ... suction tube；14 ... compression mechanical part；15a ... the first counterweight part；15b… Second counterweight part；100 ... screw compressor；201 ... fixed scroll (existing)；201b… Tabular whirlpool tooth (existing)；201h ... top ends (existing)；201k ... root (existing)；201m… Chamfered section (existing)；201n ... chamfered section (existing)；202 ... swing scroll (existing)；202b… Tabular whirlpool tooth (existing)；202h ... top ends (existing)；202k ... root (existing)；202m… Chamfered section (existing)；202n ... chamfered section (existing).
Detailed description of the invention
Hereinafter, based on accompanying drawing, the embodiment of screw compressor involved in the present invention is said Bright.Additionally, although screw compressor described herein as illustrates vertical example, but for horizontal Screw compressor also is able to apply the present invention.It addition, the following drawings including Fig. 1 is signal The accompanying drawing that is indicated, the magnitude relationship of the most each component parts is also different from practical situation.
Embodiment 1.
Fig. 1 is the longitudinal section illustrating the screw compressor involved by embodiments of the present invention 1.
Screw compressor 100 sucks the refrigerant gas of circulation in cooling cycle system, by this system The state of refrigerant gas boil down to High Temperature High Pressure is also discharged.This screw compressor 100 possesses compressor Structure portion 14, the combination of this compression mechanical part 14 has fixed scroll 1 and relative to fixed scroll Part 1 revolves round the sun the swing scroll 2 of (swing).It addition, the vortex involved by present embodiment 1 Compressor 100 is hermetic type compressor, and compression mechanical part 14 is configured in hermetic container 10.? Also it is accommodated with in this hermetic container 10 and swing scroll 2 is connected with main shaft 6 and drives this swing The motor 5 of scroll 2.In the case of vertical screw compressor 100, at hermetic container In 10, such as, compression mechanical part 14 is configured at upside and motor 5 is configured at downside.
Fixed scroll 1 possesses: seat board portion 1a；And tabular whirlpool tooth 1b, it is at seat board One face (in FIG for downside) of portion 1a erects the swirling projection of setting.It addition, pendulum Dynamic scroll 2 possesses: seat board portion 2a；And tabular whirlpool tooth 2b, it is at seat board portion 2a The face (in FIG for upside) of the side opposed with fixed scroll 1 erects the swirling of setting Projection.Tabular whirlpool tooth 2b and tabular whirlpool tooth 1b is essentially formed as same shape.Make this solid The tabular whirlpool tooth 1b and the tabular whirlpool tooth 2b swinging scroll 2 that determine scroll 1 engage each other, Thus in terms of geometry, form the discharge chambe 1f that volume changes relatively.
Herein, seat board portion 1a is equivalent to the first seat board portion in the present invention.Tabular whirlpool tooth 1b phase When the first tabular whirlpool tooth in the present invention.Seat board portion 2a is equivalent to second in the present invention Plate portion.Tabular whirlpool tooth 2b is equivalent to the second tabular whirlpool tooth in the present invention.It addition, after Ru Described, at tabular whirlpool tooth 1b and the tabular whirlpool tooth swinging scroll 2 of fixed scroll 1 Space it is formed with, in the period connected with suction inlet 1e to this space suction cold-producing medium gas between 2b Body.It addition, this space in the period connected with outlet 1d from this space discharging refrigerant gas. It addition, this space when not connecting with suction inlet 1e and outlet 1d in this space Refrigerant gas be compressed.In present embodiment 1, by the tabular in fixed scroll 1 Whirlpool tooth 1b and swing scroll 2 tabular whirlpool tooth 2b between formed space in, not with Space under the state of suction inlet 1e and the connection of outlet 1d is as discharge chambe 1f.
Utilize bolt (not shown) to be fastened by the peripheral part of fixed scroll 1 and be linked to guiding frame 4.At the peripheral part of the seat board portion 1a of fixed scroll 1, and it is being formed at fixed scroll 1 Space between tabular whirlpool tooth 1b and the tabular whirlpool tooth 2b swinging scroll 2, is provided with use In the suction tube 13 that refrigerant gas is directed into from suction inlet 1e discharge chambe 1f.In fixed scroll The central part of the seat board portion 1a of part 1 is formed to be arranged the refrigerant gas being compressed to high pressure conditions Outlet 1d gone out.And, the refrigerant gas being compressed to high pressure conditions is expelled to airtight Top in container 10, is i.e. expelled to high-pressure space 10a.As hereinafter explanation, will row The refrigerant gas gone out to this high-pressure space 10a is discharged from discharge pipe 12 by refrigerant flow path.
By for stoping the crosshead mechanism (Oldham mechanism) 9 of spinning motion to make Scroll 2 must be swung do not carry out spinning motion relative to fixed scroll 1 and be by revolution motion (oscillating motion).Fixed scroll 1 seat board portion 1a peripheral part and substantially at straight line On be formed with 2 crosshead guiding groove 1c of 1 couple.2 of 1 couple of crosshead mechanism 9 fix Side switch 9a engages with this crosshead guiding groove 1c in the way of back and forth sliding freely.It addition, at pendulum The peripheral part of the seat board portion 2a of dynamic scroll 2, with the crosshead guiding groove 1c of fixed scroll 1 There are 2 crosshead guiding groove 2c shapes the most point-blank of 1 couple of the phase contrast of 90 degree Become, 2 of 1 couple of crosshead mechanism 9 swing side switch 9b in the way of back and forth sliding freely with This crosshead guiding groove 2c engages.
Utilize the crosshead mechanism 9 constituted in the above described manner can make swing scroll 2 not rotation And it is by oscillating motion (circumnutation).It addition, at the tabular whirlpool tooth swinging scroll 2 The central part in the face of the opposition side (in FIG for downside) forming face of 2b is formed with hollow circle The oscillation bearing 2d of barrel shape.The swinging axle portion 6a arranged in the upper end of main shaft 6 is to rotate from As mode be inserted in this oscillation bearing 2d.It addition, at the seat board portion 2a swinging scroll 2 The face of the opposition side (being downside in FIG) of tabular whirlpool tooth 2b, being formed can be relative to The thrust face 2f that the thrust bearing 3a crimping of flexible frame (Compliant frame) 3 is slided. It addition, be formed as structure: be provided with discharge chambe at the seat board portion 2a swinging scroll 2 Aspirating hole 2e through with thrust face 2f for 1f, extracts out the refrigerant gas of compression midway and guides To thrust face 2f.
Herein, in order to suppress the refrigerant gas in compression process to leak from discharge chambe 1f, this enforcement Screw compressor 100 involved by mode 1 make fixed scroll 1 tabular whirlpool tooth 1b and The tabular whirlpool tooth 2b swinging scroll 2 is formed as shape.
Fig. 2 is to illustrate near the discharge chambe of the screw compressor involved by embodiments of the present invention 1 Longitudinal section.Fig. 3 is the A portion enlarged drawing in Fig. 2.It addition, Fig. 4 is the B in Fig. 2 Portion's enlarged drawing.Additionally, Fig. 2～Fig. 4 illustrates from swinging the oscillation center of scroll 2 (in other words, The axle center of main shaft part 6b of main shaft 6) pass through and along the tabular whirlpool tooth of fixed scroll 1 Compression in the cross section erecting setting direction of the tabular whirlpool tooth 2b of 1b and swing scroll 2 The cross section that the sectional area of room 1f is maximum.
In two corners of top ends 1h of the tabular whirlpool tooth 1b of fixed scroll 1, it is formed Cross section is chamfered section 1m of the chamfer shape of linearity.And, in the tabular swinging scroll 2 The both sides of the root 2k (connecting portion of seat board portion 2a and tabular whirlpool tooth 2b) of whirlpool tooth 2b are (outer All sides and inner circumferential side), it is formed with chamfered section 2n that shape is identical with the shape of chamfered section 1m. In other words, the chamfered section formed at the root 2k of the tabular whirlpool tooth 2b swinging scroll 2 2n is formed as shape: when top ends 1h of the tabular whirlpool tooth 1b in fixed scroll 1 Chamfered section 1m and this chamfered section 2n formed close to time along chamfered section 1m.
It addition, two corners of top ends 2h at the tabular whirlpool tooth 2b swinging scroll 2, It is formed with chamfered section 2m of the chamfer shape that cross section is linearity.And, in fixed scroll 1 The root 1k connecting portion of tabular whirlpool tooth 1b (the seat board portion 1a with) of tabular whirlpool tooth 1b Both sides (outer circumferential side and inner circumferential side), are formed with fall identical with the shape of chamfered section 2m of shape Corner 1n.In other words, the root 1k at the tabular whirlpool tooth 1b of fixed scroll 1 is formed Chamfered section 1n be formed as shape: when the top at the tabular whirlpool tooth 2b swinging scroll 2 Chamfered section 2m and this chamfered section 1n that end 2h is formed close to time along chamfered section 2m.
Herein, the first chamfered section during chamfered section 1m is equivalent to the present invention.Chamfered section 2m is suitable The second chamfered section in the present invention.Chamfered section 1n is equivalent to the 3rd chamfered section in the present invention. It addition, chamfered section 2n is equivalent to the 4th chamfered section in the present invention.Additionally, in present embodiment In 1, chamfered section 1m is formed with identical size (chamfer dimesion) with chamfered section 2m, chamfering Portion 1n is formed with identical size (chamfer dimesion) with chamfered section 2n.
It addition, in the screw compressor 100 involved by present embodiment 1, the most right Between space and chamfered section 2m and chamfered section 1n between chamfered section 1m and chamfered section 2n Space be set.
Specifically, as it is shown on figure 3, by under chamfered section 1m and the immediate state of chamfered section 2n , the sectional area in space formed between chamfered section 1m and chamfered section 2n be defined as Av1.Change Sentence is talked about, by by chamfered section 1m, chamfered section 2n and by the end of chamfered section 1m and chamfering The scope that the imaginary line that the end of portion 2n connects surrounds is defined as Av1.It addition, such as Fig. 4 institute Show, by chamfered section 2m with under the immediate state of chamfered section 1n, in chamfered section 2m and chamfering The sectional area in the space formed between portion 1n is defined as Av2.In other words, will by chamfered section 2m, Chamfered section 1n and the imagination being connected with the end of chamfered section 1n the end of chamfered section 2m are straight The scope that line surrounds is defined as Av2.It addition, as in figure 2 it is shown, by the sectional area of discharge chambe 1f (from Swing the oscillation center of scroll 2 to pass through and along the tabular whirlpool tooth 1b of fixed scroll 1 And the maximum in the cross section erecting setting direction of the tabular whirlpool tooth 2b swinging scroll 2 The sectional area of discharge chambe 1f) it is defined as Ac.So, Av1, Av2 and Ac are being defined In the case of, as following formula, set the screw compressor 100 involved by present embodiment 1.
0 ＜ { (Av1+Av2)/2}/Ac ＜ 1 × 10-4
As it has been described above, in present embodiment 1, chamfered section 1m and chamfered section 2m are with identical Size (chamfer dimesion) is formed, and chamfered section 1n and chamfered section 2n are with identical size (chamfering chi Very little) formed.In other words, in present embodiment 1, Av1=Av2=Av is formed as.Cause This, additionally it is possible to as following formula, express above-mentioned mathematical expression.
0 ＜ Av/Ac ＜ 1 × 10-4
Furthermore it is possible to according to the tabular whirlpool tooth 1b of fixed scroll 1 and swing scroll 2 Height H, spacing P and the thickness T of tabular whirlpool tooth 2b and obtained compression by following formula The sectional area Ac of room 1f.
Ac=(P-2 × T) × H
Again being conceived to Fig. 1, flexible frame 3 is accommodated in guiding frame 4.Flexible frame 3 exists Peripheral part is provided with barrel surface 3p and lower barrel surface 3s.Inner peripheral portion at guiding frame 4 is arranged There is upper barrel surface 4c that upper barrel surface 3p for flexible frame 3 and lower barrel surface 3s are inserted respectively With lower barrel surface 4d.Upper barrel surface 3p and lower barrel surface 3s are inserted in upper barrel surface 4c with And lower barrel surface 4d, thus and carry out diametrically to flexible frame 3 in guiding frame 4 Hold.It addition, the central part of lower barrel surface 3s of flexible frame 3 be provided with base bearing 3c and Auxiliary spindle holds 3d, the master that they rotate being driven by the rotor 5a of motor 5 diametrically Main shaft part 6b of axle 6 supports.It addition, be provided with intercommunicating pore 3e at flexible frame 3, should Intercommunicating pore 3e is the most through to the peripheral part of flexible frame 3 in the face of thrust bearing 3a.? The thrust bearing peristome 3t of the upper end open of intercommunicating pore 3e is configured to pass through with by swing scroll 2 The aspirating hole 2e of logical seat board portion 2a is opposed.
(back and forth slide it addition, be formed with face 3b at the outer circumferential side of the thrust bearing 3a of flexible frame 3 Dynamic face), crosshead mechanism annulus 9c carries out reciprocating sliding movement at this face 3b, by outside seat board The intercommunicating pore 3f that perimembranous space 2o and framework upper space 4a connects is formed as and crosshead mechanism The inner side connection of annulus 9c.Further, flexible frame 3 and at framework upper space 4a with convex It is formed with intercommunicating pore 3m between platform portion outer space 2g.It is formed with intermediate pressure at this intercommunicating pore 3m Power adjusts valve accommodation space 3n, and this intermediate pressure adjusts valve accommodation space 3n for adjusting boss The intermediate pressure of the pressure of portion's outer space 2g adjusts valve 3g, intermediate pressure adjusts valve pressing piece 3h And intermediate pressure adjusts spring 3k and receives.And, intermediate pressure adjust spring 3k with than The mode that natural length shortens is contained.
Additionally, in present embodiment 1, flexible frame 3 is constituted with guiding frame 4 split, but It is not limited thereto, it is also possible to constituted two frameworks by a framework of one.
The lower frame space formed by the lateral surface of the medial surface of guiding frame 4 Yu flexible frame 3 4b is separated by annular seal 7a, 7b up and down.Herein, flexible frame 3 outer peripheral face and At 2, position is formed with the ring-type seal groove receiving annular seal 7a, 7b, but This seal groove can also be formed at the inner peripheral surface of guiding frame 4.Lower frame space 4b is formed as Constructed as below: only to connect with the intercommunicating pore 3e of flexible frame 3, and be sealed with from aspirating hole 2e confession The refrigerant gas of the compression midway given.It addition, by swinging the seat board portion 2a of scroll 2 with soft Property framework 3 by empty to the space of outer circumferential side of thrust bearing 3a surrounded up and down, i.e. seat board peripheral part Between 2o become suck gas atmosphere (suction pressure) low-voltage space.
By hot charging or welding etc., the outer peripheral face of guiding frame 4 is fixed on hermetic container 10.? This guiding frame 4 and fixed scroll 1, the i.e. peripheral part of compression mechanical part 14 be provided with based on First path 4f of otch.It is expelled to the high-pressure space 10a's of hermetic container 10 from outlet 1d Refrigerant gas passes through and to the flowing underneath of hermetic container 10 from the first path 4f.Hermetic container The bottom of 10 becomes the store oil portion for refrigerator oil 11 storage.
The discharge pipe 12 discharged by refrigerant gas it is provided with to outside at hermetic container 10.And, The first above-mentioned path 4f is arranged at the position of the opposition side of discharge pipe 12.It addition, be provided with from The lower end central authorities of guiding frame 4 are communicated to the first drain passageway 4g of side, the first drain passageway 4g leads to discharge pipe 12.
Motor 5 drive shaft 6 rotates, and is made up of rotor 5a and stator 5b etc., wherein, This rotor 5a is fixed on main shaft part 6b of main shaft 6, and this stator 5b is fixed on hermetic container 10. Rotor 5a hot charging is fixed on main shaft part 6b of main shaft 6, and by starting to stator 5b energising Carry out rotating and drive so that main shaft 6 rotates.It addition, the upper end of main shaft 6 is formed to rotate The swinging axle portion 6a that mode freely engages with the oscillation bearing 2d swinging scroll 2, under it Side hot charging is fixed with principal axis balance counterweight 6f.
Further, being formed with main shaft part 6b in the downside of swinging axle portion 6a, this main shaft part 6b is to rotate Mode freely is held 3d engage with base bearing 3c and the auxiliary spindle of flexible frame 3.It addition, Be formed with countershaft portion 6c in the bottom of main shaft 6, this countershaft portion 6c in the way of rotatable with The supplementary bearing 8a engaging of sub-frame 8.It is provided with at main shaft 6 and is made up of the most through hole High pressure oil supply hole 6e.Therefore, the oil supply mechanism arranged in the bottom of main shaft 6 or pump machine are utilized Structure and draw refrigerator oil 11 from the oil-feed port 6d of high pressure oil supply hole 6e.High pressure oil supply hole The upper end of 6e is swinging the oscillation bearing 2d inner opening of scroll 2, the refrigerator oil 11 drawn Oscillation bearing 2d is flowed out to from the upper end open of high pressure oil supply hole 6e, thus to swinging axle portion 6a And oscillation bearing 2d is lubricated.It addition, be provided with in the horizontal at high pressure oil supply hole 6e The oil supplying hole 6g of branch, refrigerator oil 11 holds 3d from this oil supplying hole 6g supply to auxiliary spindle, Thus to base bearing 3c, auxiliary spindle holds 3d and main shaft part 6b is lubricated.
Eccentric position in the upper surface of rotor 5a and the diagonal of lower surface is respectively fixed with One counterweight part 15a and the second counterweight part 15b.It addition, oscillation bearing 2d's In outer space, the main shaft 6 in the downside of swinging axle portion 6a is fixed with aforesaid principal axis balance and joins Heavy mail 6f.These 3 counterweights part 15a, 15b, 6f are utilized to offset because swinging scroll 2 warp The imbalance of the power of the centrifugal force being carried out swinging by the swinging axle portion 6a of main shaft 6 and produce and moment, Thus obtain static equilibrium and dynamic equilibrium.
Rotor 5a is provided with the most through multiple through stream 5f.It addition, through stream 5f is to avoid the first counterweight part 15a and the side arranging position of the second counterweight part 15b Formula and arrange.Additionally, through stream 5f can also be formed as by the first counterweight part 15a with And second counterweight part 15b through.
By hot charging or welding etc., the outer peripheral face of the stator 5b of motor 5 is fixed on airtight appearance Device 10.Peripheral part at stator 5b is provided with alternate path 5g based on otch.Aforesaid first Path 4f and alternate path 5g are constituted the refrigerant gas discharged from outlet 1d to airtight The refrigerant flow path of the bottom-boot of container 10.
It addition, as it is shown in figure 1, be provided with glass terminal 10b, glass in the side of hermetic container 10 Glass terminal 10b is connected by wire 5h with the stator 5b of motor 5.
It follows that the action to the screw compressor 100 involved by present embodiment 1 illustrates.
When the starting of this screw compressor 100 and when operating, refrigerant gas is by from suction tube 13 And suction inlet 1e sucks, and enter in the tabular whirlpool tooth 1b of fixed scroll 1 and swing The space formed between the tabular whirlpool tooth 2b of scroll 2.If the swing driven by motor 5 Scroll 2 carries out eccentric circumnutation (oscillating motion), then at the tabular whirlpool of fixed scroll 1 Whirlpool tooth 1b and swing scroll 2 tabular whirlpool tooth 2b between formed space not with suction inlet 1e connects and is created as discharge chambe 1f.And, the volume of discharge chambe 1f is along with swinging vortex The eccentric circumnutation of part 2 and reduce.The refrigeration in discharge chambe 1f is made by this compression travel Agent gas is formed as high pressure conditions.Additionally, in above-mentioned compression travel, the intermediate pressure of compression midway The refrigerant gas of power is from the aspirating hole 2e intercommunicating pore via flexible frame 3 swinging scroll 2 3e and be directed to lower frame space 4b, thus maintain the intermediate pressure of this lower frame space 4b Strength atmosphere.
Discharge chambe 1f connects with outlet 1d of fixed scroll 1, thus will be via above-mentioned compression Stroke and be formed as the gas refrigerant of high pressure conditions and be expelled to hermetic container 10 from this outlet 1d High-pressure space 10a.Now, this refrigerant gas is carried out with to the sliding surface of compression mechanical part 14 The refrigerator oil 11 of lubrication mixes, and discharges from outlet 1d as mixed gas.This mixing Gas is from the first path 4f of the peripheral part setting at compression mechanical part 14 and at motor 5 Stator 5b peripheral part arrange alternate path 5g pass through and be directed to than motor 5 on the lower The bottom in the space of side, i.e. hermetic container 10.Mixed gas is being directed to hermetic container 10 Separate during Di Bu.Refrigerant gas after separating with refrigerator oil 11 flows into and is arranged at The through stream 5f of rotor 5a, passes through and further from discharge pipe 12 from the first drain passageway 4g By and discharge outside hermetic container 10.
Along with the rotation of the operating of screw compressor 100, i.e. main shaft 6, hermetic container 10 The refrigerator oil 11 of bottom flows into high pressure oil supply hole 6e from oil-feed port 6d, and at this hydraulic oil Supply hole 6e flows upward.At the refrigerator oil 11 of high pressure oil supply hole 6e flowing one Part is guided to the sky between swinging axle portion 6a upper surface and oscillation bearing 2d by the opening from upper end Between.And, swinging axle portion 6a that this refrigerator oil 11 is the narrowest in this fuel supply path and swinging axle The gap held between 2d is depressurized, and reaches higher than suction pressure and for the centre below discharge pressure Pressure, and it flow to boss portion outer space 2g.Unlike this, flow at high pressure oil supply hole 6e The part of refrigerator oil 11 guided to the high-pressure side end face of base bearing 3c from oil supplying hole 6g (being lower surface in FIG).And, the master that this refrigerator oil 11 is the narrowest in this fuel supply path Bearing 3c is depressurized with the space of main shaft part 6b and reaches intermediate pressure, and flow to boss portion equally Outer space 2g.Reach the refrigerator oil 11 of boss portion outer space 2g of intermediate pressure (because of molten Solution is generally formed as gas refrigerant and refrigerator oil in the foam of the cold-producing medium of refrigerator oil 11 2 phase fluids), from intercommunicating pore 3m and intermediate pressure adjust valve accommodation space 3n pass through time Overcoming the power of load because of intermediate pressure adjustment spring 3k, pushing and withstanding intermediate pressure adjusts valve 3g upward And it flow to framework upper space 4a.Then, refrigerator oil 11 from intercommunicating pore 3f by and be expelled to The inner side of crosshead mechanism annulus 9c.
It addition, refrigerator oil 11 is being supplied to swing thrust face 2f and the flexible box of scroll 2 It is also drawn off to crosshead mechanism after sliding part between the sliding part of the thrust bearing 3a of frame 3 The inner side of annulus 9c.And, the refrigerator oil 11 discharged from above-mentioned position is supplying to cross It is released into seat board peripheral part space after the sliding surface of head mechanism annulus 9c and key sliding surface 2o。
As described above, the spring force according to being adjusted spring 3k by intermediate pressure is adjusted with intermediate pressure The intermediate pressure of whole valve 3g exposes the authorized pressure α that area substantially determines, and utilizes following formula to convex The intermediate pressure Pm1 of platform portion outer space 2g is controlled.
Pm1=Ps+ α (Ps is for sucking atmosphere pressures i.e. low pressure)
It addition, in FIG, the aspirating hole 2e's arranged at the seat board portion 2a swinging scroll 2 The thrust bearing peristome 3t of under shed portion and the intercommunicating pore 3e arranged at flexible frame 3 i.e. on open Oral area (in FIG for the peristome of upside) connects all the time or connects off and on.Therefore, from By fixed scroll 1 and the cold-producing medium gas in the compression swinging the discharge chambe 1f that scroll 2 is formed Body, i.e. high than suction pressure and be the refrigerant gas of intermediate pressure of below discharge pressure, via Swing the aspirating hole 2e and the intercommunicating pore 3e of flexible frame 3 of scroll 2 and be directed to framework Lower space 4b.Wherein, although saying and being brought to, but owing to lower frame space 4b is by ring Closing space airtight with annular seal 7b for shape sealing member 7a, is therefore again formed as following what is called The state of breathing: when quiet rum, the pressure oscillation with discharge chambe 1f is echoed mutually, compression Room 1f and lower frame space 4b has faint air-flow in the two directions.It is as described above, According to regulation multiplying power β substantially determined by the position of the discharge chambe 1f connected and utilize following formula to frame The intermediate pressure Pm2 of frame lower space 4b is controlled.
Pm2=Ps × β (Ps is for sucking atmosphere pressures i.e. low pressure)
According to said structure, i.e. utilize 2 intermediate pressures Pm1, Pm2 and act on flexible box The pressure of the high-pressure space 10a of the lower surface 3v of frame 3 so that the directed framework of flexible frame 34 Guide and float to fixed scroll 1 side (in FIG for upside).Therefore, via thrust axis The swing scroll 2 holding 3a and pressed by flexible frame 3 floats the most upward.Its result, Swing top ends 2h of the tabular whirlpool tooth 2b of scroll 2 while with the seat board of fixed scroll 1 Portion 1a contacts while sliding, top ends 1h of the tabular whirlpool tooth 1b of fixed scroll 1 Contacting while sliding with the seat board portion 2a swinging scroll 2, thus refrigerant gas being pressed Contracting.
Herein, there is following problem in existing screw compressor: in above-mentioned compression travel, sometimes The gap formed between whirlpool tooth top end and whirlpool root portion increases, the refrigeration in compression process The amount of agent gas leakage increases, thus leakage loss aggravation.But, involved by present embodiment 1 Screw compressor 100 be formed in top ends 1h of the tabular whirlpool tooth 1b of fixed scroll 1 Chamfered section 1m, and it is formed with shape at the root 2k of the tabular whirlpool tooth 2b swinging scroll 2 Chamfered section 2n identical with the shape of chamfered section 1m.It addition, at the tabular whirlpool swinging scroll 2 Top ends 2h of whirlpool tooth 2b is formed with chamfered section 2m, and at the tabular whirlpool of fixed scroll 1 The root 1k of tooth 1b is formed with chamfered section 1n that shape is identical with the shape of chamfered section 2m.And, Achieve 0 ＜ Av/Ac ＜ 1 × 10-4Structure.Therefore, the whirlpool involved by present embodiment 1 Rotation compressor 100 can suppress the refrigerant gas in compression process from whirlpool tooth top end and whirlpool Leak between root portion such that it is able to the aggravation of suppression leakage loss.Therefore, present embodiment 1 Involved screw compressor 100 is capable of efficient screw compressor.
Fig. 5 be illustrate the Av/Ac of the screw compressor involved by embodiments of the present invention 1 with The figure of the relation of compressor performance.Herein, in Figure 5, by the whirlpool involved by present embodiment 1 The performance of rotation compressor 100 is expressed as compressor performance ratio.Compressor performance ratio is expressed as this enforcement The performance of the screw compressor 100 involved by mode 1 is relative to the performance of existing screw compressor Ratio.If compressor performance ratio is more than 100%, then the scroll compression involved by present embodiment 1 The performance of contracting machine 100 exceedes the performance of existing screw compressor.
It addition, performance described herein is the coefficient of performance (COP).The following formula property obtained can be utilized Can coefficient (COP).
COP=refrigerating capacity/consumption electric power
In other words, the performance of the screw compressor 100 involved by present embodiment 1 refers to: make Screw compressor 100 is carried, with the refrigerating capacity of regulation for the compressor of certain refrigeration cycle This refrigeration cycle is made to operate, and by the consumption electric power of screw compressor 100 except this refrigerating capacity The value of gained.The performance of existing screw compressor refers to: be equipped on by existing screw compressor The refrigeration used in the calculating of the performance of the screw compressor 100 involved by present embodiment 1 is followed Loop back path, makes this refrigeration cycle operate with the refrigerating capacity of regulation, and by existing scroll compression The electric power that consumes of contracting machine removes the value of this refrigerating capacity gained.
Additionally, for the existing scroll compression used in calculating to compressor performance ratio in Fig. 5 For machine, it is formed with fixed scroll as shown in Figure 6 and swings the tabular whirlpool tooth of scroll. In other words, two of top ends 201h of tabular whirlpool tooth 201b of fixed scroll 201 Corner, is formed with chamfered section 201m of the chamfer shape that cross section is linearity.And, swinging The both sides of the root 202k of the tabular whirlpool tooth 202b of scroll 202, being formed with cross section is circular arc Chamfered section 202n of the chamfer shape of shape.Equally, at the tabular whirlpool tooth swinging scroll 202 Two corners of top ends 202h of 202b, are formed with falling of the chamfer shape that cross section is linearity Corner 202m.And, at the root 201k of the tabular whirlpool tooth 201b of fixed scroll 201 Both sides, be formed with chamfered section 201n of the chamfer shape that cross section is arc-shaped.This existing whirlpool Rotation compressor is formed as Av/Ac=1 × 10-4。
As shown in Figure 6, the chamfer shape of the top ends of the tabular whirlpool tooth of existing screw compressor Being formed as linearity cross section, the chamfer shape of the root of tabular whirlpool tooth is formed as circular arc cross-sections. Therefore, existing screw compressor cannot make to be formed between top ends and the root of tabular whirlpool tooth Space sectional area Av reduce, it is difficult to make Av/Ac be less than 1 × 10-4.On the other hand, originally Screw compressor 100 involved by embodiment 1 is at the tabular whirlpool tooth 1b of fixed scroll 1 Top ends 1h be formed with chamfered section 1m, at the root of tabular whirlpool tooth 2b swinging scroll 2 Portion 2k is formed with chamfered section 2n that shape is identical with the shape of chamfered section 1m.It addition, swinging Top ends 2h of the tabular whirlpool tooth 2b of scroll 2 is formed with chamfered section 2m, in fixed scroll It is identical with the shape of chamfered section 2m that the root 1k of the tabular whirlpool tooth 1b of part 1 is formed with shape Chamfered section 1n.Therefore, the screw compressor 100 involved by present embodiment 1 can make at plate The sectional area Av in the space formed between top ends and the root of shape whirlpool tooth is compared with the past more Little such that it is able to realize Av/Ac ＜ 1 × 10-4Structure.Therefore, as it is shown in figure 5, this reality Execute the screw compressor 100 involved by mode 1 can suppress refrigerant gas in compression process from Leak between whirlpool tooth top end and whirlpool root portion such that it is able to the aggravation of suppression leakage loss. That is, the screw compressor 100 involved by present embodiment 1 is capable of efficient screw compressor.
Additionally, last in present embodiment 1, situations below is remarked additionally: in compression The screw compressor that the volume of room 1f is little uses the screw compressor involved by present embodiment 1 The structure of 100, so that the effect of the aggravation of suppression leakage loss increases further.
Fig. 7 be illustrate the C1m/H of the screw compressor involved by embodiments of the present invention 1 with The figure of the relation of compressor performance.Wherein, C1m is the tabular whirlpool tooth in fixed scroll 1 The chamfer dimesion C1m (with reference to Fig. 3) of chamfered section 1m that top ends 1h of 1b is formed.In this reality Executing in mode 1, chamfered section 1m is formed with identical size (chamfer dimesion) with chamfered section 2m, Therefore C1m=C2m is formed as.C2m is on the top of the tabular whirlpool tooth 2b swinging scroll 2 The chamfer dimesion C2m (with reference to Fig. 4) of chamfered section 2m that end 2h is formed.
Fig. 8 be illustrate the Dc1/Ds of the screw compressor involved by embodiments of the present invention 1 with The figure of the relation of compressor performance.Additionally, Dc1 is to utilize Equivalent Hydraulic Diameter to represent in chamfering The parameter of the sectional area Av1 in the space formed between portion 1m and chamfered section 2n.It addition, Ds is Utilize Equivalent Hydraulic Diameter to represent the parameter of the sectional area Ac of discharge chambe 1f.As it has been described above, In present embodiment 1, chamfered section 1m and chamfered section 2m are with identical size (chamfer dimesion) Being formed, chamfered section 1n is formed with identical size (chamfer dimesion) with chamfered section 2n.Therefore, The Equivalent Hydraulic of the sectional area Av2 in the space formed between chamfered section 2m and chamfered section 1n is straight Footpath Dc2 is formed as Dc2=Dc1.
Herein, it is possible to utilize following formula to obtain Equivalent Hydraulic Diameter D.
D=4 × (flow path cross sectional area)/(girth of flowing path section)
Therefore, it is possible to utilize following formula to obtain the Equivalent Hydraulic Diameter Ds of sectional area Ac of discharge chambe 1f.
Ds=4 × Ac/{2 × (P-2 × T)+2 × H)
It addition, following formula can be utilized to obtain the space formed between chamfered section 1m and chamfered section 2n The Equivalent Hydraulic Diameter Dc1 of sectional area Av1.
Dc1=4 × Av1/ (chamfered section 1m, chamfered section 2n and by the end of chamfered section 1m The length sum of the imaginary line being connected with the end of chamfered section 2n)
Additionally, in Fig. 7 and Fig. 8, by the screw compressor 100 involved by present embodiment 1 Performance to be expressed as compressor performance poor.Compressor performance difference refers to from involved by present embodiment 1 The quantized value of performance of screw compressor 100 deduct the quantization of performance of existing screw compressor The value of value gained.
In the figure 7, what top ends 1h at the tabular whirlpool tooth 1b of fixed scroll 1 was formed falls Under the state that the chamfer dimesion C1m of corner 1m is fixing, if reducing the tabular of fixed scroll 1 The height H of whirlpool tooth 1b, then the value of C1m/H increases.In other words, Fig. 7 illustrates and gets over The state that the most then volume of discharge chambe 1f is the least.It addition, in fig. 8, in chamfered section 1m And the Equivalent Hydraulic Diameter Dc1 of the sectional area Av1 in the space formed between chamfered section 2n fixes Under state, if reducing the Equivalent Hydraulic Diameter Ds, then Dc1/ of the sectional area Ac of discharge chambe 1f The value of Ds increases.In other words, Fig. 8 is also identical with Fig. 7, it is shown that then compress on the right side of more tending to The state that the volume of room 1f is the least.
The sectional area Av in the space formed between the top ends and root of tabular whirlpool tooth is identical In the case of, the capacious screw compressor of the little screw compressor of the volume of discharge chambe and discharge chambe Compare, from the amount substantially phase of the refrigerant gas of leakage between the top ends and root of tabular whirlpool tooth Deng.In other words, the sectional area in the space formed between top ends and the root of tabular whirlpool tooth In the case of Av is identical, the little screw compressor of the volume of discharge chambe is capacious with discharge chambe Screw compressor is compared, relative to the letting out of refrigerant gas of the amount of the refrigerant gas in discharge chambe Leakage quantity increases.That is, the sectional area in the space formed between top ends and the root of tabular whirlpool tooth In the case of Av is identical, the little screw compressor of the volume of discharge chambe is capacious with discharge chambe Screw compressor is compared, and leakage loss is aggravated, and efficiency reduces.
In other words, capacious for the little screw compressor of the volume making discharge chambe and discharge chambe The leakage loss equivalent of screw compressor, needs the reduction amount with the volume of discharge chambe correspondingly to reduce The sectional area Av in the space formed between top ends and the root of tabular whirlpool tooth.But, as Shown in Fig. 6, existing screw compressor is difficult to make between top ends and the root of tabular whirlpool tooth The sectional area Av in the space formed is less than certain steady state value.Therefore, existing screw compressor is in pressure The volume of contracting room is less than in the case of certain steady state value, with the reduction amount of the volume of discharge chambe correspondingly, Leakage loss is aggravated, and efficiency reduces.
On the other hand, as it has been described above, compared with existing screw compressor, present embodiment 1 institute The screw compressor 100 related to can make formation between top ends and the root of tabular whirlpool tooth The sectional area Av in space is less.Therefore, for the screw compressor involved by present embodiment 1 For 100, even if cannot suppress in existing screw compressor as the aggravation of leakage loss In the case of the volume of discharge chambe, it is also possible to correspondingly reduce with the reduction amount of the volume of discharge chambe The sectional area Av in the space formed between top ends and the root of tabular whirlpool tooth.That is, even if existing Existing screw compressor cannot suppress the volume of the such discharge chambe of aggravation of leakage loss In the case of, the screw compressor 100 involved by present embodiment 1 also is able to suppress leakage loss Aggravation such that it is able to realize efficient screw compressor.As shown in Figures 7 and 8, discharge chambe Volume is the least, and this effect is the biggest.
Embodiment 2.
In embodiment 1, by chamfered section 1m, chamfered section 1n, chamfered section 2m and chamfering Portion 2n is set to the chamfer shape that cross section is linearity.But, chamfered section 1m, chamfered section 1n, The chamfer shape of chamfered section 2m and chamfered section 2n is not limited to this shape.If chamfered section 1m and chamfered section 2n are same shape and chamfered section 2m is same shape with chamfered section 1n, Just it is obtained in that the effect shown in embodiment 1.Can make chamfered section 1m, chamfered section 1n, Chamfered section 2m and chamfered section 2n are formed as such as following such chamfer shape.Additionally, In present embodiment 2, the project not described especially is identical with embodiment 1, for identical Function, structure use identical reference to state.
Fig. 9 is to illustrate near the discharge chambe of the screw compressor involved by embodiments of the present invention 2 Longitudinal section.Figure 10 is the C portion enlarged drawing in Fig. 9.It addition, Figure 11 is the D in Fig. 9 Portion's enlarged drawing.Additionally, Fig. 9～Figure 11 illustrates from swinging the oscillation center of scroll 2 (in other words, The axle center of main shaft part 6b of main shaft 6) pass through and along the tabular whirlpool tooth of fixed scroll 1 Compression in the cross section erecting setting direction of the tabular whirlpool tooth 2b of 1b and swing scroll 2 The cross section that the sectional area of room 1f is maximum.
In two corners of top ends 1h of the tabular whirlpool tooth 1b of fixed scroll 1, it is formed Cross section is arc-shaped (more specifically, central part is convex to swing the arc-shaped of scroll 2 side) Chamfered section 1m of chamfer shape.And, at the root of the tabular whirlpool tooth 2b swinging scroll 2 The both sides of 2k, are formed with shape (more specifically, central part identical with the shape of chamfered section 1m To the opposition side of fixed scroll 1 depression arc-shaped) chamfered section 2n.In other words, exist Chamfered section 2n that the root 2k of the tabular whirlpool tooth 2b swinging scroll 2 is formed is formed as Shape: the chamfered section formed when top ends 1h of the tabular whirlpool tooth 1b in fixed scroll 1 1m and this chamfered section 2n close to time along chamfered section 1m.
It addition, two corners of top ends 2h at the tabular whirlpool tooth 2b swinging scroll 2, Being formed with cross section is that (more specifically, central part is convex to the circular arc of fixed scroll 1 side to arc-shaped Shape) chamfered section 2m of chamfer shape.And, at the tabular whirlpool tooth 1b of fixed scroll 1 The both sides of root 1k, be formed with shape identical with the shape of chamfered section 2m (more specifically, Central part to swing scroll 2 opposition side depression arc-shaped) chamfered section 1n.In other words Saying, chamfered section 1n formed at the root 1k of the tabular whirlpool tooth 1b of fixed scroll 1 is formed For following shape: when falling that top ends 2h at the tabular whirlpool tooth 2b swinging scroll 2 is formed Corner 2m and this chamfered section 1n close to time along chamfered section 2m.
It addition, in the screw compressor 100 involved by present embodiment 2, also with embodiment 1 is identical, to the space between chamfered section 1m and chamfered section 2n and chamfered section 2m and chamfering Space between portion 1n is set.
Specifically, as shown in Figure 10, by chamfered section 1m and the immediate state of chamfered section 2n Under, the sectional area in space that formed between chamfered section 1m and chamfered section 2n be defined as Av1. In other words, by by chamfered section 1m, chamfered section 2n and by the end of chamfered section 1m with fall The scope that the imaginary line that the end of corner 2n connects surrounds is defined as Av1.It addition, such as Figure 11 Shown in, by under chamfered section 2m and the immediate state of chamfered section 1n, chamfered section 2m with fall The sectional area in the space formed between the 1n of corner is defined as Av2.In other words, will be by chamfered section 2m, chamfered section 1n and the vacation that the end of chamfered section 2m is connected with the end of chamfered section 1n Think that the scope that straight line surrounds is defined as Av2.It addition, as it is shown in figure 9, by the cross section of discharge chambe 1f Long-pending (passing through from the oscillation center swinging scroll 2 and along the tabular whirlpool of fixed scroll 1 In the cross section erecting setting direction of the tabular whirlpool tooth 2b of whirlpool tooth 1b and swing scroll 2 The sectional area of maximum discharge chambe 1f) it is defined as Ac.So, define Av1, Av2 with And in the case of Ac, the screw compressor 100 involved by present embodiment 2 also with embodiment 1 is equally formed as 0 ＜ { (Av1+Av2)/2}/Ac ＜ 1 × 10-4Structure.
In present embodiment 2, chamfered section 1m and chamfered section 2m are with identical size (chamfering Size) formed, chamfered section 1n is formed with identical size (chamfer dimesion) with chamfered section 2n. In other words, in present embodiment 2, Av1=Av2=Av is formed as.It is thus possible to it is enough Above-mentioned mathematical expression is expressed as following formula.
0 ＜ Av/Ac ＜ 1 × 10-4
As above, even if in the screw compressor 100 involved by present embodiment 2, also with enforcement Mode 1 is identical, and top ends 1h at the tabular whirlpool tooth 1b of fixed scroll 1 is formed with chamfering Portion 1m, is formed with shape and chamfering at the root 2k of the tabular whirlpool tooth 2b swinging scroll 2 Chamfered section 2n that the shape of portion 1m is identical.It addition, at the tabular whirlpool tooth swinging scroll 2 Top ends 2h of 2b is formed with chamfered section 2m, at the tabular whirlpool tooth 1b of fixed scroll 1 Root 1k is formed with chamfered section 1n that shape is identical with the shape of chamfered section 2m.And, it is achieved 0 ＜ Av/Ac ＜ 1 × 10-4Structure.Therefore, the scroll compression involved by present embodiment 2 Contracting machine 100 is also identical with embodiment 1, it is possible to the refrigerant gas in suppression compression process is from whirlpool Leak between tooth top end, whirlpool and whirlpool root portion such that it is able to the aggravation of suppression leakage loss.Cause This, the screw compressor 100 involved by present embodiment 2 is also identical with embodiment 1, it is possible to Realize efficient screw compressor.
Embodiment 3.
In embodiment 1, when with cross section as linearity chamfer shape formed chamfered section 1m with And during chamfered section 2m, by chamfer dimesion C1m (with reference to Fig. 3) and the chamfered section of chamfered section 1m The chamfer dimesion C2m (with reference to Fig. 4) of 2m is set to same size.But, chamfer dimesion C1m Can also be different size with chamfer dimesion C2m.As long as chamfered section 1m and chamfered section 2n are phase Similar shape and chamfered section 2m are same shape with chamfered section 1n, are just obtained in that embodiment 1 Shown in effect.Additionally, in present embodiment 3, the project not described especially and enforcement Mode 1 is identical, uses identical reference to state for identical function, structure.
Screw compressor 100 involved by present embodiment 3 is at the tabular whirlpool of fixed scroll 1 Two corners of top ends 1h of tooth 1b, are formed with the chamfering of the chamfer shape that cross section is linearity Portion 1m.And, in the both sides of the root 2k of the tabular whirlpool tooth 2b swinging scroll 2, shape Become to have chamfered section 2n that shape is identical with the shape of chamfered section 1m.In other words, vortex is being swung Chamfered section 2n that the root 2k of the tabular whirlpool tooth 2b of part 2 is formed is formed as shape: when Chamfered section 1m formed in top ends 1h of the tabular whirlpool tooth 1b of fixed scroll 1 is fallen with this Corner 2n close to time along chamfered section 1m.
It addition, two corners of top ends 2h at the tabular whirlpool tooth 2b swinging scroll 2, It is formed with chamfered section 2m of the chamfer shape that cross section is linearity.And, in fixed scroll 1 The both sides of root 1k of tabular whirlpool tooth 1b, be formed with the shape phase of shape and chamfered section 2m Same chamfered section 1n.In other words, at the root 1k of tabular whirlpool tooth 1b of fixed scroll 1 Chamfered section 1n formed is formed as shape: when at the tabular whirlpool tooth 2b swinging scroll 2 Top ends 2h chamfered section 2m and this chamfered section 1n of being formed close to time along chamfered section 2m.
Herein, in the screw compressor 100 involved by present embodiment 3, chamfered section 1m The chamfer dimesion C2m (with reference to Fig. 4) of chamfer dimesion C1m (with reference to Fig. 3) and chamfered section 2m Different.It addition, in the screw compressor 100 involved by present embodiment 3, chamfered section 2n The chamfer dimesion C1n (with reference to Fig. 4) of chamfer dimesion C2n (with reference to Fig. 3) and chamfered section 1n Different.
In other words, the relation of C1m ≠ C2m and C1n ≠ C2n is formed as.
Even if so constituting screw compressor 100, it is also possible to make chamfered section 1m and chamfered section 2n shape Become same shape, and chamfered section 2m and chamfered section 1n can be made to be formed as same shape.Cause This, it is possible to realize 0 ＜ { (Av1+Av2)/2}/Ac ＜ 1 × 10-4Structure.Therefore, Screw compressor 100 involved by present embodiment 3 is also identical with embodiment 1, it is possible to suppression Refrigerant gas in compression process leaks between whirlpool tooth top end and whirlpool root portion, thus The aggravation of leakage loss can be suppressed.Therefore, the screw compressor 100 involved by present embodiment 3 Also identical with embodiment 1, it is possible to realize efficient screw compressor.
Further, as present embodiment 3, by constituting chamfered section 1m, chamfered section 1n, falling Corner 2m and chamfered section 2n, additionally it is possible to obtain following such effect.
The tabular whirlpool tooth 1b of fixed scroll 1 is by utilizing the process tools such as slotting cutter from becoming The periphery of tabular whirlpool tooth 1b is pruned and is formed by the material of fixed scroll 1.Now, pass through With the shape identical with chamfered section 1n that the root 1k in fixed scroll 1 is formed to process tool Front end implement chamfering, in other words, by implementing the chamfering of chamfer dimesion C1n, it is possible to solid The root 1k determining scroll 1 forms chamfered section 1n.Equally, the tabular whirlpool of scroll 2 is swung Tooth 2b also by the process tools such as slotting cutter from become swing scroll 2 material by tabular The periphery of whirlpool tooth 2b is pruned and is formed.Now, by with swing scroll 2 root Chamfering is implemented in the front end of process tool by the identical shape of chamfered section 2n that 2k is formed, in other words, By implementing the chamfering of chamfer dimesion C2n, it is possible to formed at the root 2k swinging scroll 2 Corner 2n.For cutting the tabular whirlpool tooth 1b of fixed scroll 1 and swinging scroll 2 Tabular whirlpool tooth 2b process tool for, the hardness of the material becoming processing object is the highest, It addition, the chamfer dimesion of leading section is the least, the abrasion of leading section is the fastest, and cutter life is the shortest.
Herein, such as, there is following situation: the material of fixed scroll 1 is cast iron, swing vortex The material of part 2 is aluminum (or aluminium alloy), thus fixed scroll 1 and swing scroll 2 Material is different.In this case, in chamfered section 1n and chamfered section 2n, hardness can be made The chamfer dimesion of high side increases and makes the chamfer dimesion of side that hardness is low reduce.In other words Say, can make to be formed at the chamfer dimesion C1n of chamfered section 1n of the high fixed scroll of hardness 1 Increase and make to be formed at the chamfer dimesion C2n of chamfered section 2n of the low swing scroll 2 of hardness Reduce.Furthermore it is possible to the chamfer dimesion of chamfered section 1n and chamfered section 2n correspondingly, make shape The chamfer dimesion C1m becoming chamfered section 1m of fixed scroll 1 reduces, and makes to be formed at pendulum The chamfer dimesion C2m of chamfered section 2m of dynamic scroll 2 increases.
I.e., it is possible to be set to C1n ＞ C2n and C1m ＜ C2m.
By constituting in like fashion, compared with embodiment 1, at the tabular whirlpool of fixed scroll 1 Chamfered section 1m that top ends 1h of whirlpool tooth 1b is formed and at the tabular whirlpool swinging scroll 2 The sectional area Av1 in the gap between chamfered section 2n that the root 2k of tooth 2b is formed becomes less. It addition, compared with embodiment 1, in the top ends of the tabular whirlpool tooth 2b swinging scroll 2 Chamfered section 2m that 2h is formed and the root 1k shape of the tabular whirlpool tooth 1b in fixed scroll 1 The sectional area Av2 in the gap between chamfered section 1n become becomes much larger.
That is, Av1 ＜ Av2 is formed as.
By constituting screw compressor 100 in like fashion, it is possible to suppression cuts fixed scroll 1 The front end i.e. quick abrasion of leading section of process tool of tabular whirlpool tooth 1b and cutter life hold The abrasion of the front end of the process tool easily shortened such that it is able to improve the cutter life of process tool. Further, since the cutter life of process tool can be improved, so can also process accurately The tabular whirlpool tooth 1b of fixed scroll 1.
Embodiment 4.
In embodiment 2, when with cross section as arc-shaped chamfer shape formed chamfered section 1m with And during chamfered section 2m, by chamfer dimesion (arc radius) R1m of chamfered section 1m (with reference to figure 10) it is set to identical with the chamfer dimesion of chamfered section 2m (arc radius) R2m (with reference to Figure 11) Size.But, chamfer dimesion R1m and chamfer dimesion R2m can also be different size.As long as Chamfered section 1m and chamfered section 2n are same shape and chamfered section 2m is identical with chamfered section 1n Shape, is just obtained in that the effect shown in embodiment 2.Additionally, in present embodiment 4, The project not described especially is identical with embodiment 2, uses phase for identical function, structure Same reference is stated.
Screw compressor 100 involved by present embodiment 4 is at the tabular whirlpool of fixed scroll 1 Two corners of top ends 1h of tooth 1b, are formed with the chamfering of the chamfer shape that cross section is arc-shaped Portion 1m.And, in the both sides of the root 2k of the tabular whirlpool tooth 2b swinging scroll 2, shape Become to have chamfered section 2n that shape is identical with the shape of chamfered section 1m.In other words, vortex is being swung Chamfered section 2n that the root 2k of the tabular whirlpool tooth 2b of part 2 is formed is formed as shape: when Chamfered section 1m formed in top ends 1h of the tabular whirlpool tooth 1b of fixed scroll 1 is fallen with this Corner 2n close to time along chamfered section 1m.
It addition, two corners of top ends 2h at the tabular whirlpool tooth 2b swinging scroll 2, It is formed with chamfered section 2m of the chamfer shape that cross section is arc-shaped.And, in fixed scroll 1 The both sides of root 1k of tabular whirlpool tooth 1b, be formed with the shape phase of shape and chamfered section 2m Same chamfered section 1n.In other words, at the root 1k of tabular whirlpool tooth 1b of fixed scroll 1 Chamfered section 1n formed is formed as shape: when at the tabular whirlpool tooth 2b swinging scroll 2 Top ends 2h chamfered section 2m and this chamfered section 1n of being formed close to time along chamfered section 2m.
Herein, in the screw compressor 100 involved by present embodiment 4, chamfered section 1m The chamfer dimesion R2m (with reference to Figure 11) of chamfer dimesion R1m (with reference to Figure 10) and chamfered section 2m Different.It addition, in the screw compressor 100 involved by present embodiment 4, chamfered section 2n The chamfer dimesion (circle of chamfer dimesion (arc radius) R2n (with reference to Figure 10) and chamfered section 1n Arc radius) R1n (with reference to Figure 11) difference.
In other words, the relation of R1m ≠ R2m and R1n ≠ R2n is formed as.
Even if constituting screw compressor 100 in like fashion, it is also possible to make chamfered section 1m and chamfered section 2n is formed as same shape and makes chamfered section 2m and chamfered section 1n be formed as same shape.Cause This, it is possible to realize 0 ＜ { (Av1+Av2)/2}/Ac ＜ 1 × 10-4Structure.Therefore, Screw compressor 100 involved by present embodiment 4 is also identical with embodiment 2, it is possible to suppression Refrigerant gas in compression process leaks between whirlpool tooth top end and whirlpool root portion, thus The aggravation of leakage loss can be suppressed.Therefore, the screw compressor 100 involved by present embodiment 4 Also identical with embodiment 2, it is possible to realize efficient screw compressor.
Further, by constituting chamfered section 1m, chamfered section 1n, chamfering as present embodiment 4 Portion 2m and chamfered section 2n, additionally it is possible to obtain following such effect.
The tabular whirlpool tooth 1b of fixed scroll 1 is by utilizing the process tools such as slotting cutter from becoming The periphery of tabular whirlpool tooth 1b is pruned and is formed by the material of fixed scroll 1.Now, pass through With the shape identical with chamfered section 1n that the root 1k in fixed scroll 1 is formed to process tool Front end implement chamfering, in other words, by implementing the chamfering of chamfer dimesion R1n, it is possible to solid The root 1k determining scroll 1 forms chamfered section 1n.Equally, the tabular whirlpool of scroll 2 is swung Tooth 2b also by the process tools such as slotting cutter from become swing scroll 2 material by tabular The periphery of whirlpool tooth 2b is pruned and is formed.Now, by with swing scroll 2 root Chamfering is implemented in the front end of process tool by the identical shape of chamfered section 2n that 2k is formed, in other words, By implementing the chamfering of chamfer dimesion R2n, it is possible to formed at the root 2k swinging scroll 2 Corner 2n.For cutting the tabular whirlpool tooth 1b of fixed scroll 1 and swinging scroll 2 Tabular whirlpool tooth 2b process tool for, the hardness of the material becoming processing object is the highest, It addition, the chamfer dimesion of leading section is the least, the abrasion of leading section is the fastest, and cutter life is the shortest.
Herein, such as, there is following situation: the material of fixed scroll 1 is cast iron, swing vortex The material of part 2 is aluminum (or aluminium alloy), thus fixed scroll 1 and swing scroll 2 Material is different.In such a case, it is possible to make the hardness in chamfered section 1n and chamfered section 2n high The chamfer dimesion of side increase and make the chamfer dimesion of side that hardness is low reduce.In other words, The chamfer dimesion R1n being formed at chamfered section 1n of the high fixed scroll of hardness 1 can be made to increase, And make the chamfer dimesion R2n being formed at chamfered section 2n of the low swing scroll 2 of hardness reduce. Furthermore it is possible to the chamfer dimesion of chamfered section 1n and chamfered section 2n accordingly, make to be formed at solid The chamfer dimesion R1m of chamfered section 1m determining scroll 1 reduces and makes to be formed at swing vortex The chamfer dimesion R2m of chamfered section 2m of part 2 increases.
I.e., it is possible to be set to R1n ＞ R2n and R1m ＜ R2m.
By constituting in like fashion, compared with embodiment 2, at the tabular whirlpool of fixed scroll 1 Chamfered section 1m that top ends 1h of whirlpool tooth 1b is formed and at the tabular whirlpool swinging scroll 2 The sectional area Av1 in the gap between chamfered section 2n that the root 2k of tooth 2b is formed becomes less. It addition, compared with embodiment 2, in the top ends of the tabular whirlpool tooth 2b swinging scroll 2 Chamfered section 2m that 2h is formed and the root 1k shape of the tabular whirlpool tooth 1b in fixed scroll 1 The sectional area Av2 in the gap between chamfered section 1n become becomes much larger.
That is, Av1 ＜ Av2 is formed as.
By constituting screw compressor 100 in like fashion, it is possible to suppression cuts fixed scroll 1 The front end i.e. quick abrasion of leading section of process tool of tabular whirlpool tooth 1b and cutter life hold The abrasion of the front end of the process tool easily shortened such that it is able to improve the cutter life of process tool. Further, since the cutter life of process tool can be improved, so can also process accurately The tabular whirlpool tooth 1b of fixed scroll 1.

Claims (6)

1. a screw compressor, it is characterised in that
Described screw compressor possesses:
Fixed scroll, it has the first seat board portion and stands in a face in this first seat board portion Act the first tabular whirlpool tooth arranged；
Swing scroll, its have the second seat board portion and in this second seat board portion with described The face of the side that fixed scroll is opposed erects the second tabular whirlpool tooth of setting, described first tabular Whirlpool tooth engages with described second tabular whirlpool tooth and forms discharge chambe, this swing scroll relative to Described fixed scroll carries out oscillating motion；
First chamfered section, it is formed at two corners of top ends of described first tabular whirlpool tooth；
Second chamfered section, it is formed at two corners of top ends of described second tabular whirlpool tooth；
3rd chamfered section, it is formed at the root both sides of described first tabular whirlpool tooth, and the 3rd falls The shape in corner is identical with the shape of described second chamfered section；And
4th chamfered section, it is formed at the root both sides of described second tabular whirlpool tooth, and the 4th falls The shape in corner is identical with the shape of described first chamfered section,
The chamfer dimesion of described first chamfered section is different from the chamfer dimesion of described second chamfered section.
Screw compressor the most according to claim 1, it is characterised in that
Described fixed scroll is formed by the material that hardness is different from described swing scroll,
The chamfer dimesion of the side that hardness in described 3rd chamfered section and described 4th chamfered section is high Greatly and the chamfer dimesion of the low side of hardness is little.
Screw compressor the most according to claim 1 and 2, it is characterised in that
Described first chamfered section, described second chamfered section, described 3rd chamfered section and the described 4th Chamfered section is formed as the chamfer shape that cross section is linearity.
Screw compressor the most according to claim 1 and 2, it is characterised in that
Described first chamfered section, described second chamfered section, described 3rd chamfered section and the described 4th Chamfered section is formed as the chamfer shape that cross section is arc-shaped.
Screw compressor the most according to claim 1 and 2, it is characterised in that
Pass through observing the oscillation center from described swing scroll, and along described first tabular whirlpool In the cross section erecting setting direction of whirlpool tooth and described second tabular whirlpool tooth, described discharge chambe The maximum cross section of sectional area state under,
When by described first chamfered section and being formed under the described 4th immediate state of chamfered section The sectional area in the space between described first chamfered section and described 4th chamfered section is defined as Av1, general It is formed at described second under described second chamfered section and the described 3rd immediate state of chamfered section The sectional area in the space between chamfered section and described 3rd chamfered section is defined as Av2 and by described pressure When the sectional area of contracting room is defined as Ac,
Described screw compressor is set as 0 ＜ { (Av1+Av2)/2}/Ac ＜ 1 × 10-4。
Screw compressor the most according to claim 1 and 2, it is characterised in that
Described chamfer dimesion is the size of described chamfered section.
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